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| United States Patent |
5,061,177
|
|
Knipiler
, et al.
|
October 29, 1991
|
Method and apparatus for heating a flow of gaseous fluid by successive
thermal exchanges
Abstract
The invention relates to a process and a device for indirectly heating a
flow of gaseous fluid. According to the invention, the flow of fluid to be
heated is first subjected to a first heat exchange with combustion
products, in a heat exchanger (3), and is subsequently subjected to a
second heat exchange with a heat-exchanging fluid circulating in a second
heat-exchanger (5). The flow of fluid to be heated is then circulated in a
third exchanger (7) where it is subjected to a heat exchange with the
combustion products before the latter are used at the time of the first
heat exchange. The third heat exchanger (7) can comprise radiating tubes
(51) and convection surfaces for heating the flow of fluid in circulation,
essentially by convection.
| Inventors:
|
Knipiler; Gaston (Rumilly, FR);
Suhas; Philippe (Mo Clichy, FR);
Dominique; Gosselin (Soisy Sous Montmorency, FR)
|
| Assignee:
|
Gaz de France (Paris, FR)
|
| Appl. No.:
|
497321 |
| Filed:
|
March 22, 1990 |
Foreign Application Priority Data
| Current U.S. Class: |
432/222; 34/86; 432/72; 432/181 |
| Intern'l Class: |
F24H 001/00 |
| Field of Search: |
432/72,182,181,222
34/86
110/254
|
References Cited
U.S. Patent Documents
| 3867102 | Feb., 1975 | Csathy | 110/254.
|
| 3917444 | Nov., 1975 | Carthew | 432/72.
|
| 4063590 | Dec., 1977 | McConnell | 34/86.
|
| 4152399 | May., 1979 | Germerdonk et al. | 432/72.
|
| 4169321 | Oct., 1979 | Nicholas | 34/86.
|
| 4324052 | Apr., 1982 | Boster | 34/86.
|
| 4870947 | Oct., 1989 | Kawamoto | 432/181.
|
| Foreign Patent Documents |
| 428140 | Jul., 1967 | CH.
| |
Primary Examiner: Yuen; Henry C.
Attorney, Agent or Firm: Pollock, VandeSande & Priddy
Claims
We claim:
1. A heating system for heating a flowing gaseous fluid comprising:
a first heat exchanger which has an internal volume through which a
recycling pipe meanders, for circulating combustion products for heat
exchange with said flowing fluid to be heated, said first heat exchanger
comprising a fluid inlet for admitting said flowing fluid into its
internal volume;
a second heat exchanger which has an internal volume in fluid communication
with said internal volume of said first heat exchanger and through which
at least one conduit passes for circulating a heat exchange fluid in a
heat exchange relationship with said flowing fluid to be heated; and,
a third heat exchanger which has an internal volume in fluid communication
with said internal volume of the second exchanger and with a conduit for
recovering the heated gaseous fluid, said third heat exchanger being
internally provided with tubes for circulating combustion products in a
heat exchange relationship with said flowing fluid, said tubes which are
connected to said recycling pipe extending in an internal chamber defined
externally by thermally conductive walls, said chamber being arranged on
the interior of an outer enclosure defined externally by thermally
insulating walls, said outer enclosure being, at one end, in fluid
communication with the internal volume of said second exchanger and, at
another end, in fluid communication with said internal chamber which is
connected to said conduit for recovering the heated gaseous fluid after
the latter has circulated in said internal chamber.
2. A heating system for heating a flowing gaseous fluid comprising:
a first heat exchanger which has an internal volume through which a
recycling pipe meanders, for circulating combustion products for heat
exchange with said flowing fluid to be heated, said first heat exchanger
comprising a fluid inlet for admitting said flowing fluid into its
internal volume;
a second heat exchanger which has an internal volume in fluid communication
with said internal volume of said first heat exchanger and through which
at least one conduit passes for circulating a heat exchange fluid in a
heat exchange relationship with said flowing fluid to be heated; and
a third heat exchanger which has an internal volume in fluid communication
with said internal volume of the second exchanger and with a conduit for
recovering the heated gaseous fluid, said third heat exchanger being
internally provided with tubes for circulating combustion products in a
heat exchange relationship with said flowing fluid, said tubes which are
connected to said recycling pipe comprising radiating tubes, and
convection means are arranged in a spaced-apart relationship to said
radiating tubes, said convection means being adapted to absorb the energy
radiated by said radiating tubes and to raise the temperature of said
gaseous fluid to be heated which is admitted into said third exchanger.
3. A heating system according to claim 2, wherein said convection means
consists of metal plates provided with heat exchange fins which extend
transversely in relation to the direction in which fluid to be heated is
circulated in the interior of said third exchanger.
4. A heating system according to claim 2 wherein the tubes are made of a
thermally conductive material and are connected at the exterior of said
third exchanger to a burner supplying said tubes with said combustion
products.
5. A heating system according to claim 2 wherein said tubes are U-shaped.
6. A heating system according to claim 2, wherein said second exchanger
comprises a battery of tubes which are arranged on the interior of a
thermally insulated enclosure, and means for supplying a vaporized thermal
fluid to said tubes for supplying heat to said gaseous fluid.
Description
The invention relates to a process and a device for heating a flow of
gaseous fluid, such as in particular air, for example for a pharmaceutical
application.
BACKGROUND OF THE INVENTION
The production of gas, and in particular of hot air, at high temperature
(which can be estimated a priori between 350.degree. and 450.degree. C.)
with a high throughput (for example of the order of 10,000 to 30,000
Nm.sup.3 /h) is at present frequently brought about by a certain number of
existing devices, in particular:
by direct heating of a flow of air by gaseous combustion products which are
produced from a gas burner, the flow of air and the combustion products
coming into contact and mixing;
by indirect heating of the air by means of electrical resistances;
by indirect heating of the air via a heat exchange with one or more
heat-exchanging fluids heated by gas or fuel oil.
It has, however, become apparent that these different existing systems have
a certain number of disadvantages.
First, direct heating of a flow of air in contact with gaseous combustion
products is proscribed for the manufacture of dietetic or pharmaceutical
products, given the nature of the gases produced by mixing the combustion
products and the air to be heated.
Electrical resistance heaters can only be economically used for
approximately six months per year, given the high cost of electrical power
during the coldest months of the year.
In the case of indirect heaters which function by heat exchange without
direct contact between the combustion products and the fluid to be heated,
although they represent the only devices (with the electric heaters) which
allow indirect heating of the air to a temperature higher than
approximately 300.degree. C., they nevertheless have certain
disadvantages, of which the following can be noted:
the use of walls made of refractory material, which deteriorate very
quickly as a result of operational deviations and successive restarting to
which the device is subjected;
the use likewise of special steels at the exchange stage between the
combustion products leaving the burner and the air to be heated, the use
of such steels nevertheless not preventing, in practice, frequent cracking
of the walls of the exchangers, in view of the high value of the
air/combustion products temperature gradient.
Finally, existence can be noted of major drops in pressure resulting from
the required compactness of these exchanges.
SUMMARY OF THE INVENTION
In order to remedy these shortcomings of the known devices, the invention
proposes a new type of heating system which makes it possible to increase
the efficiency of the device, in particular by reducing the temperature
deviations between the heating products and the heated products, at each
heat exchange, and by proposing a well-designed system of calorie
recovery, making it possible to produce a high-performance heating device
which is versatile, reliable and less onerous than the existing devices.
To this end, the heating process according to the invention, which is,
therefore, intended to provide for the heating of a flow of gaseous fluid,
is characterized in that:
a) the flow of fluid in question is first subjected to a first heat
exchange with combustion products which have a temperature which is higher
than that of the said flow of fluid;
b) the flow of fluid is subsequently subjected to a second heat exchange
with a heat-exchanging fluid;
c) the flow of fluid is then subjected to a third heat exchange with the
said combustion products before the latter are used at the time of the
first heat exchange.
According to an additional characteristic of the invention, it is to be
preferred in practice, in order to bring about the third heat exchange,
to transfer by radiation the calorific energy contained in the combustion
products,
to cause the energy thus radiated to be absorbed by convection surfaces,
and then to heat, essentially by convection, the said flow of fluid which
is advantageously to be made to circulate in contact with the said
convection surfaces.
According to a further characteristic of the invention, it has even proved
to be a priori preferable to carry out an additional heat exchange between
the flow of fluid leaving the heat exchange carried out according to the
above-mentioned stage b) and the flow of fluid undergoing the heat
exchange according to stage c), by then essentially making the flow of
fluid leaving the exchange carried out according to the said stage b)
circulate around and in contact with thermally conductive walls which
delimit externally an internal volume, in which the heat exchange
according to stage c) is carried out.
As mentioned at the beginning of the present description, the invention
also relates to a device for indirectly heating a flow of gaseous fluid,
such as air, this device being characterized according to the invention in
that it comprises:
a first heat exchanger which has an internal volume through which a
recycling pipe meanders, in which the combustion products for a heat
exchange with the flow of fluid to be heated circulate,
a second heat exchanger which has an internal volume in fluid communication
with the internal volume of the said first exchanger and through which at
least one conduit for heat-exchanging fluid runs, for a heat exchange with
the flow of gaseous fluid in circulation in this second exchanger,
and a third heat exchanger which also has an internal volume in fluid
communication on the one hand with the volume of the said second exchanger
and on the other hand with a conduit for the recovery of the heated
gaseous fluid, at least one tube, which is provided for the circulation of
combustion products in heat exchange with the said flow of gaseous fluid
circulating in the third exchanger, meandering in the internal volume of
this latter and being connected to the said recycling pipe for the
combustion products.
BRIEF DESCRIPTION OF THE DRAWINGS
The characteristics of the invention which have just been set out, as well
as other additional characteristics, emerge in a more detailed manner from
the following description which is made with reference to the attached
drawings which are given by way of non-limitative examples and in which:
FIG. 1 is a schematic overall view of a possible embodiment of the heating
device according to the invention, and
FIG. 2 illustrates schematically an embodiment detail of an internal part
of the third exchanger.
DETAILED DESCRIPTION OF THE INVENTION
With reference in the first instance to FIG. 1, a heating device for
gaseous fluid, reference number 1, is illustrated.
The device 1 consists of three successive enclosures which form heat
exchangers 3, 5, 7 and are arranged in series, one after another.
As illustrated, the first exchanger 3 consists of an enclosure with walls 6
which can be metal and define a chamber 8 with an internal volume into
which, at one end, an intake duct 9 opens for the admission of the flow of
fluid to be heated (such as air).
On the interior of the chamber 8, at least one recycling pipe 11 meanders,
which can have exchange fins 12 and in which it is envisaged to make
circulate the gaseous combustion products for the purpose of an indirect
heat exchange with the flow of fluid passing through the chamber 8, and
this before these same combustion products are evacuated from the
exchanger 3 via the recovery duct 13 to which the pipe 11 is connected.
Essentially opposite the fluid intake duct 9, the internal chamber 8 of the
first exchanger 3 is connected, by means of a connecting duct 17, to one
end of the internal, chamber 15 of the second exchanger 5, so as to ensure
the supply of this exchanger with preheated gaseous fluid.
This exchanger 5 can in particular be made in such a manner that its
internal chamber 15 is delimited by metal walls 19 which are externally
covered with a thermally insulating casing 21.
On the interior of the chamber 15, a heat exchange battery 23 is arranged,
which consists of a number of tubes 25 (possibly with fins) which extend
essentially perpendicularly to the direction of circulation of the gaseous
fluid in the chamber 15 (direction indicated by the arrow 27). These
different tubes 25 are connected at their two opposite ends to two
collectors 29, 31. A supply pipe 33 for heat-exchanging fluid is connected
to the intake collector 29. In particular, it can be envisaged to use
water vapor or synthetic oil vapor as heat-exchanging fluid or thermal
fluid. In this case, it is preferable to connect the collector 31 to an
evacuation conduit 35 for the vapor condensate, a drain valve 36
advantageously permitting control of the evacuation of this condensate.
In order likewise to achieve control of the throughput of thermal fluid
admitted into the exchange battery 23, it has proved to be preferable to
arrange a control valve 38 on the in favor of supply pipe 33.
Towards its end which is opposite to the duct 17, the chamber 15
communicates with the internal volume of the third heat exchanger 7, by
means of a connection channel 37 which opens on the one hand into the
lower part of the chamber 15 and on the other into the upper part of the
internal volume of the third exchanger 7.
As is clearly illustrated, also in FIG. 1, the internal volume of this
exchanger 7 is divided into a large internal chamber 39 which is delimited
externally by thermally conductive (in particular metal) walls 41 which
are themselves arranged at a certain distance from a thermally insulated
external enclosure 43.
In practice, the connection channel 37 between the exchangers 5 and 7
passes through the enclosure 43 locally and in the upper part to open at
one end of the space 45, the width 1 of which is to be sufficient to
ensure a correct circulation of the flow of fluid around and in contact
with the external conductive walls 41 of the internal chamber 39.
Essentially opposite the connection duct 37, and preferably in the bottom
part, the chamber 39 communicates with the space 45 by means of a
communication opening 47 in such a manner that the gaseous fluid, which
has circulated in this space 45, can penetrate into the interior of the
chamber 39 in order to undergo there a further heat exchange with the
combustion products circulating within the exchange tubes 51 which are
connected, upstream, to burners 53 which can in particular be powered by
fuel gas and oxidant air.
In order to limit the problems associated with faulty functioning of a
burner, it has been envisaged according to the invention preferably to use
a number of exchange tubes 51, each of which is connected, on the exterior
but in the immediate vicinity of the enclosure 43, to a burner 53.
As exchange tubes 51, it is preferable to use radiating tubes, for example
U-shaped tubes which extend mainly in the internal chamber 39 before being
connected in each case, passing through the enclosure 43, to a recovery
pipe 55 which is provided to recycle the combustion products leaving the
third exchanger 7 in the direction of the pipe 11 of the first exchanger
3.
In FIG. 1, it is also to be observed that, in order to provide for the
evacuation and the recovery of the gaseous flow which is heated in the
third exchanger 7, the chamber 39 is connected locally and preferably in
the top part, to a recovery conduit 57. Advantageously, this conduit 57 is
connected to the chamber 39 in a place which is capable of encouraging a
circulation of the gaseous flow to be heated there, which is on the whole
oriented in a transverse direction in relation to that in which the tubes
51 extend, which are then preferably arranged essentially parallel to one
another.
In order to encourage this circulation of the fluid to be heated, the
chamber 39 can furthermore be provided, at the connection of the conduit
57, with a deflector 59.
It has also proved to be useful to attach to this assembly a control system
which consists of a heat probe 61 which is in direct contact with the
recovery conduit 57 and is connected to a control unit 63 which is capable
of acting on the one hand on the automatic valve 38 for control of the
throughput of thermal fluid through the supply pipe 33 and on the other
hand on another automatic valve 65 for control of the supply throughput,
for example of fuel gas, to the burners 53.
Since an important characteristic of the invention resides in the design of
the third heat exchanger 7, special attention has moreover been given to
the production of the latter and in particular to the configuration of the
radiating tubes 51.
These latter can of course be made with heat exchange fins, as shown at 67
in FIG. 1, these fins then preferably extending transversely in relation
to the general direction (shown at 69) of the flow of gaseous fluid on the
interior of the chamber 39.
However, FIG. 2 shows a cut-away schematic illustration in a perspective
view of the chamber 39 in which elbowed radiating tubes 51' are arranged,
extending essentially parallel over the entire length of the chamber.
These radiating tubes 51', which can have a metal radiating surface, are
in the case in point without fins. On the other hand, between two
consecutive tubes and at a distance from each of them, convection means
are provided, for example in the form of plates 71 with metal convection
surfaces, adapted to absorb the energy radiated by the tubes, so as to
heat in particular by convection, upon contact with these plates, the
fluid (represented schematically by the double arrow 73) which is still
admitted into the chamber 39 through the opening 47.
Preferably, the convection plates 71 are provided on their two opposite
surfaces with heat exchange fins 75 which advantageously extend
transversely in relation to the direction in which a circulation of the
fluid is encouraged on the interior of the chamber 39.
It is to be noted that, as illustrated in FIG. 2, the plates 71 are
preferably to be arranged so as to constitute, in relation to one another,
baffles which lengthen the course of the fluid on the interior of the
chamber 39 and encourage its mixing, the fluid thus recovering the
calories concentrated around the plates and between the fins 75, which can
in particular be metal.
Other types of structurally different convection surfaces of the plates 71
can of course be envisaged, without leaving the scope of the invention.
The principle of functioning of the device, which has been described above,
is briefly described below.
This functioning is the following:
The gaseous fluid to be heated, for example air, is first of all introduced
into the first exchanger 3 by means of the admission duct 9. This fluid,
which can for example be admitted at the ambient temperature of 25.degree.
C., is heated in contact with the serpentine formed by the transverse pipe
11 on the interior of which, therefore, the combustion products
originating from the burners 53 circulate, after these products have lost
a portion of their calories by heat exchange in the third exchanger 7.
While these same combustion products are evacuated via the recovery duct
13, the flow of fluid passes from the chamber 8 of the first exchanger to
the chamber 15 of the second exchanger 5 where it is again heated by
indirect heat exchange, essentially through the exchange walls of the
battery of tubes 25 on the interior of which, therefore, a vaporized
thermal, fluid circulates, such as for example water vapor which can be
admitted under a pressure of the order of 10 to 15 bar and at a
temperature of the order of 230.degree. to 260.degree. C.
In this manner, the gaseous fluid which enters into the second exchanger 5
at a temperature of, for example, 60.degree. to 80.degree. C., can leave
it at 180.degree. or even 200.degree. C., indeed possibly more, it being
possible to adapt the heating temperature gradient by virtue of the
control unit 63 which is preferably to be programmed so that the
variations in the rates of heat release are first and foremost absorbed by
the vaporized thermal fluid, thus making it possible to reduce to a
minimum sudden thermal variations at the burners 53 and the radiating
tubes 51 of the third exchanger 7.
Leaving the second exchanger 5, the flow of fluid, already heated by two
successive heat exchanges, is then admitted into the peripheral space 45
of the third exchanger 7.
Given the positioning of the access opening 47 to the internal chamber 39
of this third exchanger 7, the fluid to be heated has to first of all,
therefore, circulate essentially in contact with the thermally conductive
external walls of this chamber 39, thus recovering, in particular by
convection, a portion of the calories contained in the chamber 39 and
released via the wall 41 of this latter either by the flow of fluid in
circulation or by the radiating tubes 51 or 51' and/or by the convection
plates 71 and their fins 75 (see FIG. 2).
However, the essential part of the heat exchange carried out on the
interior of the third exchanger 7 is carried out on the interior of the
chamber 39 when the flow of fluid comes to circulate in the immediate
environment of the tubes 51 (or 51'), through which it is possible to
transfer, by radiation, the calorific energy contained in the combustion
products just leaving the burners 53 (usually at a temperature of
approximately 800.degree. to 1,200.degree. C.).
By means of the provision of convection plates 71 (preferably with fins),
the energy thus radiated can be absorbed and then restored to the fluid
which is thus heated in the chamber 39 by convection, by circulating in
contact with the convection surfaces provided to this end, before being
evacuated at a temperature which can be estimated as a rule between
350.degree. and 450.degree. C., via the recovery conduit 57 where the heat
probe 61 permits the control unit 63 to measure out the supply, on the one
hand of vaporized thermal fluid to the second exchanger 5 and on the other
hand of fuel to the burners 53, via the valves 38 and 65 respectively,
preferably with priority given to the vapor circuit of the exchanger 5.
It is to be noted that with such a heating process, without direct contact
between the gaseous fluid to be heated and the heat-exchanging fluids for
heating, it is possible to deliver from the device a hot fluid at high
temperature, which is free of pollution and can be used, for example, in
the agro-alimentary or pharmaceutical industry, in particular for the
drying of products or indeed for different thermal processes.
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